EP1575742B1 - Gearset, in particular for electric hand machine tools - Google Patents

Gearset, in particular for electric hand machine tools Download PDF

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Publication number
EP1575742B1
EP1575742B1 EP03813519A EP03813519A EP1575742B1 EP 1575742 B1 EP1575742 B1 EP 1575742B1 EP 03813519 A EP03813519 A EP 03813519A EP 03813519 A EP03813519 A EP 03813519A EP 1575742 B1 EP1575742 B1 EP 1575742B1
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EP
European Patent Office
Prior art keywords
output shaft
gearwheel
output
driver
radial
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP03813519A
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German (de)
French (fr)
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EP1575742A1 (en
Inventor
Joachim Schadow
Juergen Wiker
Peter Stierle
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP1575742A1 publication Critical patent/EP1575742A1/en
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/001—Gearings, speed selectors, clutches or the like specially adapted for rotary tools
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/124—Elastomeric springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/14—Construction providing resilience or vibration-damping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/14—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising conical gears only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/0006—Vibration-damping or noise reducing means specially adapted for gearings
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19633—Yieldability in gear trains

Definitions

  • the invention relates to a transmission, in particular for electric hand tool machines, according to the preamble of patent claim 1.
  • Made of sintered gears pairs of gears have production due to the disadvantage of large tolerances, causing a loud running noise and has a negative effect on the life.
  • This coupling part is formed like a flange sleeve and has in the region of its sleeve at its inner and outer circumferential longitudinal grooves, with which teeth which are provided on both bevel gear halves, cooperate.
  • the coupling part is provided with recesses into which engage cams located on the two axially opposed surfaces of the two bevel gear halves.
  • the transmission according to the invention in particular for electric hand tool machines, with the features of claim 1 has the advantage that by the between the output gear and the output shaft activated damping elements, which are preferably made of rubber or a rubber-like material with high damping factor and in the circumferential direction or Tangential act, not only existing in the gear pair tolerances, especially pitch errors, profile deviations and concentricity errors are compensated, causing transmission noise and vibrations caused by the transmission drop significantly, but that also acting on the teeth, very high start-up forces when switching on the drive shaft rotating drive motor due to the inertia of the drive and the driven masses occur, as well as occurring during operation of the teeth load peaks are reduced.
  • damping elements which are preferably made of rubber or a rubber-like material with high damping factor and in the circumferential direction or Tangential act, not only existing in the gear pair tolerances, especially pitch errors, profile deviations and concentricity errors are compensated, causing transmission noise and vibrations caused by the transmission drop significantly, but that also acting on the teeth, very high
  • the damping elements can be inserted into the pockets or connected to the radial webs, e.g. be splashed on the radial webs, be.
  • FIG. 1 in an exploded view angle gear for an electric hand tool as an exemplary embodiment of a general transmission has an electric motor driven by a drive shaft 11, a on the drive shaft 11 rotatably seated drive gear 12, which is designed here as bevel pinion with pinion teeth 121, a meshing with the drive gear 12 output gear 13, which is formed as a crown gear with spur gear teeth 131, and driven by the output gear 13 Output shaft 14 on.
  • the output gear 13 is seated without play rotatably and axially immovably on the output shaft 14, wherein it is supported in the axial direction on the one hand on an output shaft 14 formed on the annular shoulder 15 (FIG.
  • the driver 16 has a the output shaft 14 enclosing ring 17 and a plurality, in the exemplary embodiment three, offset in the circumferential direction radial webs 18, which are integrally formed with the ring 17 or instead of a plurality of parts.
  • the output shaft 14 carries in the region of the ring 17 two diametrically arranged axial grooves 19 and the ring 17 has two diametrically arranged, on the inner annular surface projecting cam 20, which dive into the axial grooves 19 positively.
  • the radial webs 18 are offset in the embodiment by the same circumferential angle and each project centrally into pockets 21, which are formed in the output gear 13 at the same rotational angle distance as the radial webs 18 from each other.
  • the pockets 21 are bounded in the circumferential direction in each case by radially aligned side walls 211.
  • two damping elements 22 of resilient material, such as rubber, are arranged, wherein each damping element 22 rests on the one hand on a radial web 18 and on the other hand on a side wall 211 of the pocket 21.
  • the damping elements 22 are inserted either in the assembly of the transmission in the pockets 21 or previously firmly connected to the radial webs 18.
  • the output gear 13 When switching on the electric motor, the torque is transmitted from the drive shaft 11 via the drive gear 12 to the output gear 13. Since the output gear 13 is rotatably seated on the output shaft 14, the output gear 13 can first rotate by compressing the rearward in the direction of rotation damping element 22 by a few degrees, then via the radial webs 18 to rotate the driver 16 and - since the driver 16 rotatably on the output shaft 14 is seated - to drive the output shaft 14.
  • the damping elements 22 is thus achieved that in the output gear 13 already takes place a rotation without a rotation occurs on the output shaft 14. This delay reduces the maximum occurring acceleration and extends the time until the full idle speed of the output shaft 14 is reached.
  • the high load on the teeth between the drive gear 12 and output gear 13 is reduced during startup.
  • the pockets 21 are designed with a rectangular clear cross-section, which are bounded in the circumferential direction of two radial, planar side walls 211.
  • the projecting into the pockets 21 radial webs 18 have a rectangular cross-section.
  • the damping elements 22 may have any geometry. They are in the embodiment e.g. formed as a roller-shaped, elastic body, which are aligned parallel to the axis of the output shaft 14.
  • modified geometries of the pockets 21 and the radial webs 18 are possible, wherein the number of radial webs 18 and correspondingly the number of pockets 21 can be varied.
  • FIG. 3 shows a matrix which shows possible combinations of pocket geometries and radial web geometries.
  • FIG. 3 shows a matrix which shows possible combinations of pocket geometries and radial web geometries.
  • All bag profiles A, B, C and D can be combined with the corresponding radial bar profiles in lines 1, 2, 3 and 4.
  • the matrix is self-explanatory, so that only a few special features are pointed out:
  • the pocket 21 as in the embodiment of Figs. 1 and 2, planar side walls.
  • the side walls are provided with bulges, which may be either arcuate or angular. These bulges take on the deformation of the damping elements 22, a portion of the material of the damping elements 22, so that the spring characteristics of the damping elements 22 are improved.
  • the damping elements 22 are still supported on the radial web 18 and on the two side walls 211 of the pockets 21.
  • the damping elements 22 are formed either spherical or cylindrical, extending in the radial direction in the roll shape.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Gear Transmission (AREA)
  • Gears, Cams (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Getriebe, insbesondere für Elektrohandwerkzeugmaschinen, nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a transmission, in particular for electric hand tool machines, according to the preamble of patent claim 1.

Bei Getrieben für Elektrohandwerkzeugmaschinen kommen aus Kostengründen gesinterte Zahnräder mit einer Spiral- oder Geradverzahnung zum Einsatz. Auf geschnittene Zahnräder, deren Fertigungskosten relativ hoch sind, wird nur dann zurückgegriffen, wenn bei hochwertigen Geräten hohe Anforderungen an die Laufruhe gestellt werden. Zahnräder aus Kunststoff, die ähnlich kostengünstig wie Sinter-Zahnräder herstellbar sind, können nur kleine Drehmomente übertragen und finden daher bei Elektrohandwerkzeugmaschinen nur in wenigen Ausnahmefällen Anwendung.In gearboxes for electric hand tool machines sintered gears with a spiral or straight toothing are used for cost reasons. On cut gears whose production costs are relatively high, is only resorted to when high-quality equipment high demands are made on the smoothness. Gears made of plastic, which are similarly cost-effective as sintered gears produced, can only transmit small torques and therefore find in electric hand tool only in a few exceptional cases application.

Aus Sinter-Zahnrädern zusammengestellte Zahnradpaare haben fertigungsbedingt den Nachteil großer Toleranzen, was ein lautes Laufgeräusch verursacht und sich negativ auf die Lebensdauer auswirkt.Made of sintered gears pairs of gears have production due to the disadvantage of large tolerances, causing a loud running noise and has a negative effect on the life.

Es ist ein Getriebe der eingangs genannten Art für einen Winkelschleifer bekannt (DE 39 22 552 A), mit einem auf einer Antriebswelle drehfest sitzenden Antriebs-Ritzel und einem mit diesem Ritzel kämmenden und davon angetriebenen Kegelzahnrad für den Antrieb einer Abtriebswelle. Das Kegelzahnrad ist in zwei axiale Hälften geteilt. Die untere Kegelzahnradhälfte ist drehfest mit der Abtriebswelle verbunden. Die obere Kegelzahnradhälfte hat keinen unmittelbaren Kontakt mit der Abtriebswelle. Zwischen beiden Kegelzahnradhälften ist axial ein flächiges schwingungsdämpfendes Bauteil eingefügt, das aus schwingungsdämpfenden Material wie Gummi von geeigneter Härte od. dgl. besteht. Die auf der Abtriebswelle angebrachte Kegelzahnradhälfte ist mit der anderen, antriebsseiten Kegelzahnradhälfte, die mit dem Ritzel kämmt, über das schwingungsdämpfende Bauteil in der Gestaltung als Kupplungsteil mechanisch verbunden.It is a transmission of the type mentioned for an angle grinder known (DE 39 22 552 A), with a rotatably seated on a drive shaft drive pinion and meshing with this pinion and driven therefrom bevel gear for driving an output shaft. The bevel gear is divided into two axial halves. The lower bevel gear half is rotatably connected to the output shaft. The upper bevel gear half has no direct contact with the output shaft. Between two bevel gear halves a flat vibration damping member is inserted axially, the od of vibration damping material such as rubber of suitable hardness. The like. There is. The bevel gear half mounted on the output shaft is mechanically connected to the other side of the bevel gear half meshing with the pinion through the vibration damping member in the configuration as the coupling part.

Dieses Kupplungsteil ist flanschhülsenartig ausgebildet und weist im Bereich seiner Hülse an seinem Innen- und Außenumfang Längsnuten auf, mit denen Zähne, die an beiden Kegelzahnradhälften vorgesehen sind, zusammenwirken. Das Kupplungsteil ist mit Ausnehmungen versehen, in die an den beiden axial einander gegenüberliegenden Flächen der beiden Kegelzahnradhälften befindliche Nocken eingreifen. Durch dieses Bauteil in Form des aus schwingungsdämpfendem Material bestehenden Kupplungsteils werden während des Bearbeitungsvorganges von der Schleifscheibe auf die Abtriebswelle übertragene Vibrationen weitgehend abgedämpft, so dass auf das mit der oberen Kegelzahnradhälfte kämmende Ritzel allenfalls nur noch in sehr geringem Ausmaß von der Bearbeitungsseite herrührende Schwingungen übertragen werden. Entsprechendes soll auch für eine Schwingungsübertragung über die Lagerung der Abtriebswelle auf das Maschinengehäuse gelten. Das Kupplungsteil ist mit beiden Kegelradhälften durch einen Vulkanisationsprozess mechanisch verbunden.This coupling part is formed like a flange sleeve and has in the region of its sleeve at its inner and outer circumferential longitudinal grooves, with which teeth which are provided on both bevel gear halves, cooperate. The coupling part is provided with recesses into which engage cams located on the two axially opposed surfaces of the two bevel gear halves. By this component in the form of consisting of vibration damping material coupling part vibrations transmitted during the machining process of the grinding wheel to the output shaft are largely damped, so that are transmitted to the meshing with the upper bevel gear half pinion at best only to a very small extent originating from the machining side vibrations , The same should also apply to a vibration transmission via the bearing of the output shaft to the machine housing. The coupling part is mechanically connected to both bevel gear halves by a vulcanization process.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Getriebe, insbesondere für Elektrohandwerkzeugmaschinen, mit den Merkmalen des Anspruchs 1 hat den Vorteil, daß durch die zwischen dem Abtriebs-Zahnrad und der Abtriebswelle eingeschalteten Dämpfungselemente, die vorzugsweise aus Gummi oder einem gummiähnlichen Material mit hohem Dämpfungsfaktor hergestellt sind und in Umfangsrichtung bzw. Tangentialrichtung wirken, nicht nur in der Zahnradpaarung vorhandene Toleranzen, insbesondere Teilungsfehler, Profilabweichungen und Rundlauffehler, kompensiert werden, wodurch Getriebegeräusche und vom Getriebe verursachte Vibrationen deutlich sinken, sondern dass auch die auf die Verzahnung wirkenden, sehr hohen Anlaufkräfte, die beim Einschalten des die Antriebswelle drehenden Antriebsmotors durch die Trägheit des Antriebs und der angetriebenen Massen auftreten, sowie die im Betrieb an der Verzahnung auftretenden Lastspitzen reduziert werden.The transmission according to the invention, in particular for electric hand tool machines, with the features of claim 1 has the advantage that by the between the output gear and the output shaft activated damping elements, which are preferably made of rubber or a rubber-like material with high damping factor and in the circumferential direction or Tangential act, not only existing in the gear pair tolerances, especially pitch errors, profile deviations and concentricity errors are compensated, causing transmission noise and vibrations caused by the transmission drop significantly, but that also acting on the teeth, very high start-up forces when switching on the drive shaft rotating drive motor due to the inertia of the drive and the driven masses occur, as well as occurring during operation of the teeth load peaks are reduced.

Insgesamt führt dies zu einer großen Laufruhe bei Sinter- Zahnrädern und unabhängig von dem Typ der Zahnräder (gesintert oder geschnitten) infolge der verringerten mechanischen Belastung zu einer hohen Lebensdauer des Getriebes. Die Dämpfungselemente können dabei in die Taschen eingelegt oder mit den Radialstegen verbunden, z.B. auf die Radialstege aufgespritzt, werden.Overall, this leads to a great quiet running in sintered gears and regardless of the type of gears (sintered or cut) due to the reduced mechanical stress to a long service life of the transmission. The damping elements can be inserted into the pockets or connected to the radial webs, e.g. be splashed on the radial webs, be.

Durch die in den weiteren Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Anspruch 1 angegeben Getriebes möglich.The measures listed in the further claims advantageous refinements and improvements of the claim 1 transmission are possible.

Zeichnungdrawing

Die Erfindung ist anhand eines in der Zeichnung dargestellten Ausführungsbeispiels in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Fig. 1
ein Winkelgetriebe für eine Elektrohandwerkzeugmaschine in Explosionsdarstellung,
Fig. 2
eine perspektivische Ansicht des zusammengesetzten Getriebes in Fig. 1,
Fig. 3
eine Matrix zur übersichtlichen Zusammenstellung möglicher Taschen- und Radialsteggeometrien im Getriebe gemäß Fig. 1 und 2.
The invention is explained in more detail in the following description with reference to an embodiment shown in the drawing. Show it:
Fig. 1
an angular gear for an electric hand tool machine in exploded view,
Fig. 2
1 is a perspective view of the assembled transmission in FIG. 1,
Fig. 3
a matrix for a clear summary of possible pocket and Radialsteggeometrien in the transmission of FIG. 1 and 2.

Beschreibung des AusfiihrungsbeispielsDescription of the exemplary embodiment

Das in Fig. 1 in Explosionsdarstellung skizzierte Winkelgetriebe für eine Elektrohandwerkzeugmaschine als Ausführungsbeispiel für ein allgemeines Getriebe weist eine von einem Elektromotor antreibbare Antriebswelle 11, ein auf der Antriebswelle 11 drehfest sitzendes Antriebs-Zahnrad 12, das hier als Kegelritzel mit Ritzelverzahnung 121 ausgeführt ist, ein mit dem Antriebs-Zahnrad 12 kämmendes Abtriebs-Zahnrad 13, das als Tellerrad mit Stirnverzahnung 131 ausgebildet ist, sowie eine vom Abtriebs-Zahnrad 13 angetriebene Abtriebswelle 14 auf. Das Abtriebs-Zahnrad 13 sitzt spielfrei drehbar und axial unverschieblich auf der Abtriebswelle 14, wobei es sich in axialer Richtung einerseits an einer auf der Abtriebswelle 14 ausgebildeten Ringschulter 15 (Fig. 1) und andererseits an einem Mitnehmer 16 abstützt, der auf die Abtriebswelle 14 aufgepreßt ist und zusätzlich formschlüssig mit der Abtriebswelle 14 verbunden ist. Der Mitnehmer 16 weist einen die Abtriebswelle 14 umschließenden Ring 17 sowie eine Mehrzahl, im Ausführungsbeispiel drei, in Umfangsrichtung versetzt angeordnete Radialstege 18 auf, die mit dem Ring 17 einstückig ausgebildet sind oder statt dessen mehrteilig sind. Die Abtriebswelle 14 trägt im Bereich des Rings 17 zwei diametral angeordnete Axialnuten 19 und der Ring 17 zwei diametral angeordnete, an der inneren Ringfläche vorstehende Nocken 20, die formschlüssig in die Axialnuten 19 eintauchen. Die Radialstege 18 sind im Ausführungsbeispiel um gleiche Umfangswinkel versetzt und ragen jeweils mittig in Taschen 21 hinein, die im Abtriebs-Zahnrad 13 in gleichem Drehwinkel-Abstand wie die Radialstege 18 voneinander eingeformt sind. Die Taschen 21 sind in Umfangsrichtung jeweils durch radial ausgerichtete Seitenwände 211 begrenzt. In jeder Tasche 21 sind zwei Dämpfungselemente 22 aus federelastischem Material, z.B. Gummi, angeordnet, wobei jedes Dämpfungselement 22 einerseits an einem Radialsteg 18 und andererseits an einer Seitenwand 211 der Tasche 21 anliegt. Die Dämpfungselemente 22 werden entweder bei der Montage des Getriebes in die Taschen 21 eingelegt oder zuvor mit den Radialstegen 18 fest verbunden.The sketched in Fig. 1 in an exploded view angle gear for an electric hand tool as an exemplary embodiment of a general transmission has an electric motor driven by a drive shaft 11, a on the drive shaft 11 rotatably seated drive gear 12, which is designed here as bevel pinion with pinion teeth 121, a meshing with the drive gear 12 output gear 13, which is formed as a crown gear with spur gear teeth 131, and driven by the output gear 13 Output shaft 14 on. The output gear 13 is seated without play rotatably and axially immovably on the output shaft 14, wherein it is supported in the axial direction on the one hand on an output shaft 14 formed on the annular shoulder 15 (FIG. 1) and on the other hand on a driver 16 which on the output shaft 14th is pressed and is additionally positively connected to the output shaft 14. The driver 16 has a the output shaft 14 enclosing ring 17 and a plurality, in the exemplary embodiment three, offset in the circumferential direction radial webs 18, which are integrally formed with the ring 17 or instead of a plurality of parts. The output shaft 14 carries in the region of the ring 17 two diametrically arranged axial grooves 19 and the ring 17 has two diametrically arranged, on the inner annular surface projecting cam 20, which dive into the axial grooves 19 positively. The radial webs 18 are offset in the embodiment by the same circumferential angle and each project centrally into pockets 21, which are formed in the output gear 13 at the same rotational angle distance as the radial webs 18 from each other. The pockets 21 are bounded in the circumferential direction in each case by radially aligned side walls 211. In each pocket 21, two damping elements 22 of resilient material, such as rubber, are arranged, wherein each damping element 22 rests on the one hand on a radial web 18 and on the other hand on a side wall 211 of the pocket 21. The damping elements 22 are inserted either in the assembly of the transmission in the pockets 21 or previously firmly connected to the radial webs 18.

Bei Einschalten des Elektromotors wird das Drehmoment von der Antriebswelle 11 über das Antriebs-Zahnrad 12 auf das Abtriebs-Zahnrad 13 übertragen. Da das Abtriebs-Zahnrad 13 drehbar auf der Abtriebswelle 14 sitzt, kann sich das Abtriebs-Zahnrad 13 zunächst unter Zusammendrücken des in Drehrichtung hinten liegenden Dämpfungselements 22 um einige Grad verdrehen, um dann über die Radialstege 18 den Mitnehmer 16 zu verdrehen und - da der Mitnehmer 16 drehfest auf der Abtriebswelle 14 sitzt - die Abtriebswelle 14 anzutreiben. Durch die Dämpfungselemente 22 wird also erreicht, daß im Abtriebs-Zahnrad 13 bereits eine Verdrehung stattfindet, ohne daß an der Abtriebswelle 14 eine Verdrehung auftritt. Durch diese Verzögerung wird die maximal auftretende Beschleunigung reduziert und die Zeit bis zum Erreichen der vollen Leerlaufdrehzahl der Abtriebswelle 14 verlängert. Damit wird die hohe Belastung auf die Verzahnung zwischen Antriebs-Zahnrad 12 und Abtriebs-Zahnrad 13 beim Anlauf reduziert.When switching on the electric motor, the torque is transmitted from the drive shaft 11 via the drive gear 12 to the output gear 13. Since the output gear 13 is rotatably seated on the output shaft 14, the output gear 13 can first rotate by compressing the rearward in the direction of rotation damping element 22 by a few degrees, then via the radial webs 18 to rotate the driver 16 and - since the driver 16 rotatably on the output shaft 14 is seated - to drive the output shaft 14. By the damping elements 22 is thus achieved that in the output gear 13 already takes place a rotation without a rotation occurs on the output shaft 14. This delay reduces the maximum occurring acceleration and extends the time until the full idle speed of the output shaft 14 is reached. Thus, the high load on the teeth between the drive gear 12 and output gear 13 is reduced during startup.

Im Betrieb der Elektrohandwerkzeugmaschine wird durch die Dämpfungselemente 22 das Aufeinanderschlagen der Zähne zwischen der Ritzelverzahnung 121 und Stirnverzahnung 131 abgedämpft, was zu einer deutlichen Reduzierung des Getrieberasseln führt, das bei herkömmlichen Elektrohandwerkzeugmaschinen insbesondere im An- oder Auslauf der Elektrohandwerkzeugmaschine deutlich zu vernehmen ist. Hierfür sind insbesondere die in Drehrichtung vorderen Dämpfungselemente 22 ausschlaggebend, die die der Drehrichtung entgegengesetzt auftretenden Stöße dämpfen.In operation of the electric hand tool machine 22, the impact of the teeth between the pinion teeth 121 and spur toothing 131 is damped by the damping elements, which leads to a significant reduction of the gear rattle, which is clearly heard in conventional electric hand tool machines, especially in the arrival or departure of the electric power tool. For this purpose, in particular in the direction of rotation front damping elements 22 are crucial, which dampen the opposite direction of rotation occurring shocks.

Beim Arbeiten mit der Elektrohandwerkzeugmaschine kommt es vor, daß das Werkzeug kurzzeitig im Werkstück einhakt. Z.B. beim Arbeiten mit Winkelschleifern und Trennscheiben ist dies ein häufig auftretender Arbeitsfall. Bei diesem Einhaken, was einem kurzzeitigen Blockieren des Werkzeugs gleichkommt, werden extreme Kräfte auf die Verzahnungen 121, 131 zwischen Antriebs-Zahnrad 12 und Abtriebs-Zahnrad 13 ausgeübt. Diese Kraftspitzen werden durch die Dämpfungselemente 22 wirksam abgeschwächt, was zu einer Reduzierung des Rückschlagmoments, das der Bediener aufnehmen muß, führt und somit für den Bediener einen Komfortgewinn darstellt. Insgesamt werden die mechanischen Belastungen auf das Getriebe reduziert, was zu höheren Standzeiten und spürbar höherem Komfort führt, da Getriebeschwingungen, Getriebestöße u. ä. nur stark vermindert auf das Maschinengehäuse übertragen werden.When working with the electric hand tool machine, it happens that the tool hooks briefly in the workpiece. For example, when working with angle grinders and cutting wheels this is a common case of work. In this hooking, which amounts to a brief blocking of the tool, extreme forces are exerted on the teeth 121, 131 between the drive gear 12 and the output gear 13. These force peaks are effectively attenuated by the damping elements 22, resulting in a reduction of the kickback torque that the operator must absorb, and thus represents a comfort gain for the operator. Overall, the mechanical loads on the transmission are reduced, which leads to higher service life and noticeably higher comfort, since transmission vibrations, Transmission shocks u. Ä. Only greatly reduced transferred to the machine housing.

In dem in Fig. 1 und 2 dargestellten Ausführungsbeispiel sind die Taschen 21 mit rechteckförmigem lichten Querschnitt ausgeführt, die in Umfangsrichtung von zwei radialen, ebenen Seitenwänden 211 begrenzt sind. Die in die Taschen 21 hineinragenden Radialstege 18 haben einen rechteckförmigen Querschnitt. Die Dämpfungselemente 22 können eine beliebige Geometrie aufweisen. Sie sind beim Ausführungsbeispiel z.B. als walzenförmige, elastische Körper ausgebildet, die parallel zur Achse der Abtriebswelle 14 ausgerichtet sind. Selbstverständlich sind modifizierte Geometrien der Taschen 21 und der Radialstege 18 möglich, wobei auch die Anzahl der Radialstege 18 und entsprechend die Anzahl der Taschen 21 variiert werden kann.In the embodiment shown in Fig. 1 and 2, the pockets 21 are designed with a rectangular clear cross-section, which are bounded in the circumferential direction of two radial, planar side walls 211. The projecting into the pockets 21 radial webs 18 have a rectangular cross-section. The damping elements 22 may have any geometry. They are in the embodiment e.g. formed as a roller-shaped, elastic body, which are aligned parallel to the axis of the output shaft 14. Of course, modified geometries of the pockets 21 and the radial webs 18 are possible, wherein the number of radial webs 18 and correspondingly the number of pockets 21 can be varied.

In Fig. 3 ist eine Matrix dargestellt, die mögliche Kombinationen von Taschengeometrien und Radialsteggeometrien zeigt. ln der obersten Zeile sind verschiedene lichte Profile der Taschen 21 und in der linken Spalte verschiedene Profile der Radialstege 18 angegeben. Dabei können alle Taschenprofile A, B, C und D mit den entsprechenden Radialstegprofilen in den Zeilen 1, 2, 3 und 4 kombiniert werden. Die Matrix ist selbsterklärend, so daß lediglich auf ein paar Besonderheiten hingewiesen wird:FIG. 3 shows a matrix which shows possible combinations of pocket geometries and radial web geometries. In the top row different clear profiles of the pockets 21 and in the left column different profiles of the radial webs 18 are indicated. All bag profiles A, B, C and D can be combined with the corresponding radial bar profiles in lines 1, 2, 3 and 4. The matrix is self-explanatory, so that only a few special features are pointed out:

In Spalte C weist die Tasche 21, wie in dem Ausführungsbeispiel der Fig. 1 und 2, ebene Seitenwände auf. ln den Spalten A, B und D sind die Seitenwände mit Ausbuchtungen versehen, die entweder bogenförmig oder eckig ausgeführt sein können. Diese Ausbuchtungen nehmen bei der Deformation der Dämpfungselemente 22 ein Teil des Materials der Dämpfungselemente 22 auf, so daß die Federeigenschaften der Dämpfungselemente 22 verbessert werden. Die Profile der Radialstege 18 können, wie in der linken Spalie-dargestellt, rechteckig, keilförmig, und rechteckig mit Einbuchtungen (Zeile 3) und Ausbuchtungen (Zeile 4) ausgeführt werden. In allen Kombinationsfällen von Taschenprofil und Radialstegprofil stützen sich die Dämpfungselemente 22 nach wie vor am Radialsteg 18 und an den beiden Seitenwänden 211 der Taschen 21 ab. In den Kombinationen A/1. A/2, A/3, B/3, C/3 und D/3 sind die Dämpfungselemente 22 entweder kugelförmig oder walzenförmig ausgebildet, wobei sie sich bei Walzenform in Radialrichtung erstrecken.In column C, the pocket 21, as in the embodiment of Figs. 1 and 2, planar side walls. In the columns A, B and D, the side walls are provided with bulges, which may be either arcuate or angular. These bulges take on the deformation of the damping elements 22, a portion of the material of the damping elements 22, so that the spring characteristics of the damping elements 22 are improved. The profiles of the radial webs 18, as shown in the left-hand spalie, rectangular, wedge-shaped, and rectangular with indentations (line 3) and bulges (Line 4). In all combination cases of pocket profile and radial web profile, the damping elements 22 are still supported on the radial web 18 and on the two side walls 211 of the pockets 21. In combinations A / 1. A / 2, A / 3, B / 3, C / 3 and D / 3, the damping elements 22 are formed either spherical or cylindrical, extending in the radial direction in the roll shape.

Claims (7)

  1. Gearing, in particular for portable electric power tools, comprising a drive gearwheel (12) sitting on a drive shaft (11) in a rotationally fixed manner, an output gearwheel (13) meshing with said drive gearwheel (12) and driving an output shaft (14), and elastic damping elements (22) which are arranged between the output gearwheel (13) and the output shaft (14) and are held on a driver (16) connected to the output shaft (14) in a rotationally and axially fixed manner, the output gearwheel (13) being rotatable relative to the output shaft (14) and having pockets (21) which are defined by radial side walls (211) and are arranged so as to be offset from one another in the circumferential direction and in which the damping elements (22) rest in contact with the radial side walls (211), characterized in that the driver (16) has a ring (17) sitting on the output shaft (14) and a number of radial webs (18) which correspond to the number of pockets (21) in the output gearwheel (13) and of which one each projects into a respective pocket (21), and in that two or more damping elements (22) resting in place on each side of the radial web (18) are provided in each pocket (21), of which damping elements (22) each is supported on the radial web (18) and on a radial side wall (211) of the pocket (21).
  2. Gearing according to Claim 1, characterized in that the output gearwheel (13) is supported in the axial direction on the one hand on an annular shoulder (15) formed on the output shaft (14) and on the other hand on the driver (16).
  3. Gearing according to Claim 1, characterized in that the ring (17) of the driver (16) is pressed onto the output shaft (14).
  4. Gearing according to one of Claims 1 to 3, characterized in that the ring (17) of the driver (16) is connected to the output shaft (14) in a positive-locking manner.
  5. Gearing according to one of Claims 1 to 4, characterized in that the radial side walls (211) of the pockets (21) have recesses in the region in contact with the damping elements (22).
  6. Gearing according to one of Claims 1 to 5, characterized in that the radial webs (18) of the driver (16), at least in their region projecting into the pockets (21), have a rectangular profile, with or without niches or bulges, or a wedge-shaped profile.
  7. Gearing according to one of Claims 1 to 6, characterized by its design as angular gearing, in which the output gearwheel (13) is designed as a crown wheel having a spur tooth system (131) and the drive gearwheel (12) is designed as a bevel pinion having a pinion tooth system (121).
EP03813519A 2002-12-19 2003-07-21 Gearset, in particular for electric hand machine tools Expired - Lifetime EP1575742B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10259519 2002-12-19
DE10259519A DE10259519A1 (en) 2002-12-19 2002-12-19 Gearboxes, in particular for electric hand machine tools
PCT/DE2003/002427 WO2004056535A1 (en) 2002-12-19 2003-07-21 Gearset, in particular for electric hand machine tools

Publications (2)

Publication Number Publication Date
EP1575742A1 EP1575742A1 (en) 2005-09-21
EP1575742B1 true EP1575742B1 (en) 2007-03-28

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EP03813519A Expired - Lifetime EP1575742B1 (en) 2002-12-19 2003-07-21 Gearset, in particular for electric hand machine tools

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US (1) US20060191365A1 (en)
EP (1) EP1575742B1 (en)
CN (1) CN100467232C (en)
DE (2) DE10259519A1 (en)
WO (1) WO2004056535A1 (en)

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Also Published As

Publication number Publication date
DE50306932D1 (en) 2007-05-10
EP1575742A1 (en) 2005-09-21
DE10259519A1 (en) 2004-07-01
US20060191365A1 (en) 2006-08-31
CN1717301A (en) 2006-01-04
CN100467232C (en) 2009-03-11
WO2004056535A1 (en) 2004-07-08

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